Wheel slip control apparatus having quick closing valves

ABSTRACT

The invention concerns a quick closing valve, in particular a disc valve for antiskid devices on street vehicles with a closing member controlling a flow of pressure medium from a chamber of higher pressure to a chamber of lower pressure.

nited States Patent 1191 Bait et ai. [45] Ja 29, 1974 WHEEL SLIP CONTROLAPPARATUS [56] References Cited HAVING QUICK CLOSING VALVES UNITEDSTATES PATENTS [75] Inventors: Alfred Klatt, Wettbergen; Fritz 2,980,3854/1961 Hunter et al 251/25 Isemhagen, L Lutz w 3,016,065 1/1962 Stampflil37/625.64 Misburg; Erich Reinecke, Beinhorn, FOREIGN PATENTSORAPPLICATIONS of Germany 900,153 7/1962 Great Britain .7 25l/6l.l [73]Assignee: Westinghouse Bremsen-und Apparatebau GmbH, Hannover, PrimaryExaminer-Henry T. Klinksiek Germany Attorney, Agent, or Firm- Ralph W.Mclntire, Jr.;

. P 22 Filed: 061. 24, 1972 w F 1 [21] Appl. No.: 300,284 [57] ABSTRACTThe invention concerns a quick closing valve, in par- [52] CL 251/25251/61 1 ticuiar a disc valve for antiskid devices on street vehi- [51]Int CL a 31/145 cles with a closing member controlling a flow of pres-[58] Field 612 122 sure medium from a chamber of higher pressure to achamber of lower pressure.

9 Claims, 3 Drawing Figures 1 WHEEL SLIP CONTROL APPARATUS HAVING QUICKCLOSING VALVES BACKGROUND OF THE INVENTION High requirements arefrequently imposed on valves of this type with respect to the shortestpossible closing time. This feature previously has been achieved byreducing the mass of the moving parts of the valve and by pre-unloadingthe closing member using a spring or a static pressure. However, thesemeasures are unsatisfactory for achieving extremely short closing timessuch as are necessary, for instance, on nonskid devices of streetvehicles.

The invention has the purpose of creating a valve of the type named thatcan bemoved to its closed position as rapidly as possible and isdistinguished by simple construction and a reliable-mode of operation.

SUMMARY OF INVENTION This task is solved according to the invention bythe fact that the quick closing valve display means installed in thepath of flow of the pressure medium for producing a reduction of thefluid pressure force acting on one side of the closing member to therebyincrease the effectiveness of the fluid, pressure force acting on theother side which force acts in the closing direction.

In this way it is possible to achieve an effective unloading of theclosing member in the closing direction and thus obtain a considerableshortening of the closing time with the aid of devices automaticallyoperative when the valve is to be closed which do not influence the massof the moving valve parts or to only an insignificant degree.

In a further design'according to the invention, the means for producinga reduction of the fluid pressure force on the one side are designed asa flow-deflecting body which is.carried by the closing member, andinstalled at a distance from the closing member in such a way that thereduction in force produced is dependent on the velocity of flow. Thisreduction of force is effective to cause snap-acting movement of theclosing member in the closing direction. Preferably, the flowdeflectingbody is formed byafunnel-shaped piece tapering in the closing directionof the valve.

It is advantageous if the closing member that constitutes a valve hasformed integral with one side thereof a coaxial concave dished conicalsurface which is tapered in the direction of a valve seat and thereforeis curved in such a way that when the valve is open, the flow ofpressure medium against the concave dished conical surface causes thedirection of flow to be turned while maintaining a roughly constanteffective cross section area of flow or one which increases in theclosing direction. In this way, the flow of the pressure medium from theintake chamber to the outlet boring is unhindered and its direction offlow turned without special space-consuming separate turning means.

The means for producing a reduction of the fluid pressure force as theresult of flow can also be formed according to the invention as animpingement body rigidly attached to the closing member and space adistance from it so that this body is immersed in the flow of thepressure medium. Advisably, the impingement body is a circular plateinstalled coaxially with the closing member and spaced a chosen distancefrom it.

It is further provided according to the invention that in the case ofapressure-medium activated quick closing valve whose activating memberhas one side acted on by the pressure in the higher pressure chamber,the means for producing the reduction of the fluid pressure force on theother side is formed by a throttle or choke installed between the higherpressure chamber on the one side and a valve intake chamber on the otherside and bordered by the closing member. Thus, the activating member onits one side is capable of being acted on by the pressure in front ofthe throttle and on its opposite side by the pressurein the valve intakechamber which pressure is that behind or on the outlet side of thethrottle.

It is possible within the limits of the invention to use the means forproducing a flow-dependent pressure force according to the designdiscussed above either individually or in combination.

In order further to shorten the closing time of the valves of thepressure-medium activated quick closing valves, in another embodiment ofthe invention, it is provided that the closing member serves simultaneously as the activating member, whereby the closing and activatingmember is advisably formed by a membrane or diaphragm formed of anelastic material.

A further shortening of the closing times can be achieved by having themembrance supported on its activation side against a roughly cone-shapedhousing seat in such a way that the membrane displays an increasingeffective area as it is moved away from the housing seat during anactivation stroke.

In the following, various examples of the invention are more closelyexplained with reference to the drawing.

FIG. 1 shows an antiskid device for street vehicles with a brakingpressure control valve arrangement consisting of a supply valve and arelease valve, partially depicted by diagram.

FIG. 2 shows a time-pressure'diagram for the antiskid device accordingto FIG. 1.

FIG. 3 shows another variant or a second embodiment of the supply valvefor the antiskid device according to FIG. 1.

The antiskid device shown in FIG. 1 displays a braking pressure controlvalve device 1 composed ofa supply valve 2 and a release'valve 3.

The supply valve 2 is installed in a pipe 6, 7, 8 leading from acompressed air container or reservoir 4 to a brake cylinder 5. Thesupply valve 2 has a brake valve 9 connected in front of it.

The release valve 3 is installed in a pipe 10, 11 leading from brakecylinder 5 to atmosphere.

Both valves 2 and 3 are designed as pressure-medium activateddiaphragm-type valves and can be opened and closed by operation ofmagnetic valves 12 and 13. The magnetic valves 12 and 13 are operated bysolenoids. The exciter circuits of the coils of these solenoids areconnected to an electrical type of wheel deceleration and accelerationdetector device 14. Therefore, when the wheel deceleration oracceleration reaches certain chosen values, these magnetic valves areoperated in the manner hereinafter described.

The supply valve 2 consists of a valve housing 15 with two housing partsl6, 17 between which a diaphragm 18 that serves both as the closing andalso the activating member, and is composed of an elastic material, ismounted. The diaphragm l8 separates the control chamber 19 and a valveintake chamber 20 from one another and has a centric attachment 21 whichforms a disc valve that is movable into contact with a seat 22 formed ona flange that is integral with a guide bushing 23.

The control chamber 19 can be connected to pipe 7 via housing borings25, 26, magnetic valve 12, and housing boring 27. The inlet chamber 20is connected to pipe 7 via the housing boring 25 and a channel 28serving as a throttle or choke. Thus, the control chamber 19 can beacted on by the pressure in front of or at the inlet of the throttle orchoke 28, while the inlet chamber 20 can be acted on by the pressurebehind or at the outlet of the throttle.

Diaphragm 18 is supported on its activation or upper side against aroughly conical housing seat 24.

A throttle member 30 with an annular piston 31 and a tubular projection32 has a sliding fit along guide bushing 23 and is displaceable againsta spring 34 in a housing boring 33, the projection 32 being capable offorming a throttle 32, 35 with the housing projection 35.

An annular disc 36 installed in the intake chamber 20, and mountedbetween the two housing parts 16, 17, has a projection 37 with afunnel-shaped taper in the closing direction, serving as a flowdeflecting body, which projection encloses the diaphragm 18 serving asthe closing member and is mounted at such a distance from this diaphragmthat it turns the flow of air flowing from the housing boring 25 to thehousing boring 33 through inlet chamber 20 away from the diaphragm area38 of diaphragm 18, viewed in the closing direction, thus producing areduction of pressure which unloads the diaphragm 18 on its lower sidethus making it snap acting as it moves inthe closing direction.

The projection 21 of the diaphragm 18 is designed as a body ofrevolution that forms a dished cone with a concavely curved surface 39serving as a closing area, whose curvature is so selected such that astream of air flowing from housing boring 25 to housing boring 33through inlet chamber 20 is turned by this curved surface 39 while aroughly constant effective cross section of flow or one increasing inthe closing direction is maintained. The cross section of flow isbordered on one side by the curved surface 39 and on the opposite sideby the surface of the flange 22 that is integral with the upper end ofthe guide bushing 23.

Diaphragm 18 has a metallic reinforcement plate 40 serving to reinforcean unloading spring 41. The spring force of the unloading spring 41which acts against the elastic force of membrane 18 acting in theopening direction is so dimensioned that when the valve is notactivated, the diaphragm l8 maintains a stable open positron.

The release valve 3 consists of a valve housing 45 with two housingparts 46, 47, between which a diaphragm 48 is mounted as a closing andactivating member. Diaphragm 48 separates a control chamber 49 and anintake chamber 50 from one another and displays a centric projection 51which forms a disc valve that is movable into contact with a valve seat52 formed on housing part 47.

The control chamber 49 can be connected with a source of compressed air,such as the reservoir 4, via pipe 6, pipe and corresponding passageway53, the magnetic valve 13, and a housing boring 54. The intake chamber50 is connected to the brake cylinder 5 via a housing boring 55 and pipe10. An annular disc 56 mounted in the intake chamber 50 is designed andinstalled in the same manner as annular disc 36 for the intake valve 15.Its funnel-shaped projection 57 encloses the diaphragm 48 serving as theclosing member and is installed at such a distance from this diaphragmthat it turns a stream of air flowing from housing boring 55 to housingboring or exhaust port 11 through intake chamber 50 away from the frontor lower surface of diaphragm 48, viewed in the closing direction, thusproducing a reduction of pressure which unloads the diaphragm 48 in theclosing direction.

Projection 51 of diaphragm 48 is designed in the same manner asprojection 21 of diaphragm l8 and therefore need not be describedfurther. Diaphragm 48 also, like diaphragm 18, has a metallicreinforcement plate 59 serving to reinforce an unloading spring 60corresponding to spring 41 of the inlet valve 2.

The mode of action of the antiskid device according to FIG. 1 isexplained below with reference to the timepressure curve according toFIG. 2:

When the brake is not activated, the antiskid mechanism is in theposition showing FIG. 1 in which the supply valve 2 is open and releasevalve 3 is closed. Accordingly, control chamber 19 of supply valve 2 isevacuated so that diaphragm 18 is held precisely in the stable openposition by its own elastic force due to the counteracting unloadingspring 41.

Control chamber 49 of release valve 3 on the other hand, is charged withair via pipe 6, pipe and passageway 53, open magnetic valve 13, andhousing boring 54, so that diaphragm 48 is acted on by an activationpressure and its projection 51 serving as a valve disc, is pressedagainst the valve seat 52 on housing part 47.

If a braking application is initiated by activation of brake valve 9,then the compressed air container 4 is connected to the brake cylinder 5via pipes 6, 7, housing boring 25, throttle channel or choke 28, inletchamber 20, housing boring 33, and pipe 8 and in the brake cylinder 5produces an increasing braking pressure P corresponding to the curve P P(FIG. 2). Thus a stream of air is produced which flows from a chamber ofhigher pressure (compressed air container 4) to a chamber of lowerpressure (brake cylinder 5) through inlet chamber 20 of the supply valve2 and is there deflected by the funnel-shaped projection 37 of theannular disc 36 away from the lower surface 38 of the diaphragm 18, theprojection 37 thus serving as a flow deflecting body.

This flow of air then carries the air from between the funnel-shapedprojection 37 and the lower surface 38 of the diaphragm 18 so that areduction of pressure dependent on the velocity of flow of the air isproduced in this chamber which reduction of pressure has an unloadingeffect on diaphragm 18 in the closing direction. In this way, thepressure prevailing in inlet chamber 20 is now rendered, to a greatdegree, inactive with respect to diaphragm 18, so that the latter isunloaded in the closing direction when the compressed air flows throughsupply valve 2.

The flow of air is subsequently turned by projection 21 of diaphragm 18in the direction ofthe valve seat 22 due to the special shape of thesurface 39 and reaches boring housing 33, whereby the cross section offlow bordered by the surface 39 and the opposite area of the flange ofthe guide bushing 23 and increasing in the direction of flow provide anunhindered flow through valve 21, 22.

At the same time, piston 31 of throttle member 30 is acted on on bothsides by the pressure of the compressed air flowing so that it remainsheld by the pressure of the closing spring 34 in the nonthrottlingposition shown, while braking pressure is built up in brake cylinder 5.

If the rate of wheel deceleration at this time exceeds a certain chosenvalue which value is an indication that the wheel skid or slip thresholdhas been reached, the current generated by the detector device 14 inresponse to this rate of wheel deceleration and supplied to the solenoidcoils of the magnetic valves 12 and 13 is reduced to substantially zero.Consequently, the upper valves 61 are unseated and the lower valves 62are seated by springs 63.

When the lower valve 62 of magnetic valve 13 is thus seated,communication is closed between reservoir 4 and the control chamber 49of the release valve 3. When the upper valve 61 of magnet valve 13 isthus unseated, fluid under pressure is vented fromchamber 49 toatmosphere via bore .54 and past the now open valve 61. Since the brakecylinder 5 is connected to chamber 50 via pipe and bore 55, this fluidunder pressure acting in chamber 50 and on the lower side of diaphragm48 deflects this diaphragm upward so that it is unseated from valve seat52 against the yielding resistance of spring 60. Fluid under pressure inthe brake cylinder 5 now flows to atmosphere via pipes 8 and 10, bore55, chamber 50, past valve seat 52 and exhaust passageway 11. Thus, thepressure in the brake cylinder 5 is quickly reduced corresponding to thecurve P P shown in FIG. 2.

it should be noted that when the diaphragm 48 is unseated from the valveseat 52, fluid under pressure present in the bore 33 in supply valve 2may flow to atmosphere via pipes 8 and 10, bore 55, past valve seat 52and exhaust passageway 11. This flow of fluid under pressure toatmosphere tends to reduce the-pressure in chamber of supply valve 2.

Since valves 61 of magnetic valves 12 and 13 are unseated and valves 62of'these magnet valves are seated simultaneously by the springs 63 whenthe current in the solenoid coils of these magnet valves is reduced tosubstantially zero when the wheel'begins to skid or slip,

the fluid under pressure present in the bore of supply valve 2 will flowto' chamber 19 via bore 26, past now open valve 61 of magnetic valve 12,and bore 27.

The supply of fluid under pressure to chamber 19 acts on the uppersideof diaphragm 18 and deflects it downward until it contacts valveseat 22 thus quickly cutting off flow of fluid under pressure from thereservoir 4and brake valve 9 to the brake cylinder 5. This closing ofthe supply valve 2 takes place in a very short time, since the pressureon the surface 39 on the lower side of diaphragm 18 has been reduced bythe flow of fluid under pressure past the funnel-shaped projection 37.

Furthermore, it should be noted that the pressure supplied to thechamber 19 is always higher than that supplied to the chamber 20 via thechannel 28 which serves as a throttle or choke. Consequently, thisdifferential of pressure aids in providing for the quick closing of thesupply valve 2.

Moreover, the extremely rapid closing of disc valve 21 integral with thediaphragm 18 against the valve seat 22 is also facilitated by-the actthat this valve has a single moving member (diaphragm I8 and centerattachment 21) having a very small mass. Also, it should be noted thatas the diaphragm 18 is deflected downward, it is moved away from theconical seat 24 on housing part 16 thereby increasing its effective areathat is subject to fluid under pressure in chamber 19. Consequcntly, thediapragm 18 is moved downward into contact with valve seat 22 with asnap action.

Fluid under pressure is retained in the chamber 20 subsequent to theseating ofdiaphragm 18011 valve seat 22, it being noted that fluid underpressure is supplied to this chamber 20 from the brake valve 9 via pipe7, bore 25, and channel 28 which serves as a choke. However, since therelease valve 3 is open, fluid under pressure can flow from the bore 33to atmosphere via pipes 8 and 10, bore 55, chamber 50, past valve seat52 and exhaust passageway 11. Consequently, the pressure on the lowerside of the piston 31 is reduced so that the trapped pressure in chamber20 and acting on the upper side of this piston 31 moves it and thetubular projection 32 that is integral therewith downward against theyielding resistance of spring 34. As tubular projection 32 is thus moveddownward toward housing projection or boss 35, it reduces thecross-sectional area of the passageway through which fluid underpressure may flow to the brake cylinder 5 thereby providing a throttle.

Now let it be assumed that when the pressure in the brake cylinder 5 hasbeen reduced to the value indicated by P in FIG. 2, the deceleration ofthe wheel is above the value that indicates that the skid or slipthreshold has been reached. Consequently, the current now generated bythe detector device 14 and supplied to the solenoid coil of the magnetvalve 13 of release valve 3 is sufficient to cause operation of thisvalve 13 to seat its upper valve 61 and unseat its lower valve 62.However, this current is not enough to cause operation of the magnetvalve 12.

This seating of upper valve 61 and unseating oflower valve 62 of magnetvalve 13 closes the communication between control chamber 49 andatmosphere and opens a communication between the reservoir 4 and thischamber 49.

The supply of fluid. under pressure from the reservoir 4 to the controlchamber 49 causes rapid downward deflection ofdiaphragm 48 to theposition shown in which it abuts the valve seat 52 thereby closingcommunication between chamber 50 and atmosphere. This quick closing ofthe release valve 3 occurs for the same reasons as hereinbeforementioned in connection with the quick closing of the supply valve 2.

Upon the closing of release valve 3, a residual pressure P P ismaintained in the brake cylinder 5, while the wheel of the vehiclecontinues to turn. Thus, by cutting off the flow of fluid under pressurefrom the brake cylinder 5 to atmosphere at the time wheel decelerationreaches a value above that which indicates that the skid or slipthreshold has been reached, the braking force absorption capacity isbetter utilized at the end of the brake cylinder pressure reduction thanwould be the case if brake cylinder pressure were reduced to zero.

If now the wheel acceleration exceeds a chosen value that indicates thatthe spinning threshold of the wheel has been reached, the currentgenerated by the detector device 14 and supplied to the solenoid coil ofthe magnet valve 12 of supply valve 2 is sufficient to cause operationof this magnet valve 12 to seat its upper valve 61 and unseat its lowervalve 62.

This seating of upper valve 61 and unseating of lower valve 62 of magnetvalve 12 closes the communication between the reservoir 4 and controlchamber 49 and vents the fluid under pressure in this chamber 49 toatmosphere. When control chamber 49 is thus vented, the fluid underpressure present in the chamber is rendered effective to deflectdiaphragm 18 upward from seating contact with valve seat 22 to theposition shown in FIG. 1 thereby opening a communication between thereservoir 4 and the brake cylinder 5.

This opening of the supply valve 2 results in a resupply of fluid underpressure to the brake cylinder 5 to cause an increase of the pressuretherein. However, since piston 31 and tubular projection 32 have beenmoved downward from the position shown in FIG. 1, in the mannerhereinbefore explained, so that projection 32 and boss 35 constitute athrottle or choke, the buildup of pressure in the brake cylinder 5 willoccur more slowly, than if piston 31 and projection 32 occupied theposition shown in FIG. 1. This slow build-up of brake cylinder pressurebetter utilizes the braking force absorption capacity of the wheel inthat it prevents a reoccurrence of slipping of the wheel.

The supply valve according to FIG. 3 differs from the supply valveaccording to FIG. 1 only in that its closing member is also unloaded bymeans of an impingement disc. Parts formed identical to those in FIG. 1are characterized with reference numbers increased by 100 in comparisonto the corresponding numbers in FIG. 1.

Diaphragm 118 displays connecting plug 160 mounted coaxially in anextension of projection 21, carrying on its end protruding into guidesleeve 123 a circular metallic impingement disc 161 connected to it andthus to diaphragm 118 immovably. The diameter of impingement disc 161 isso selected that a flow of air through the guide sleeve 123 and housingboring 133 takes place without throttling.

The impingement disc 161 is so mounted in guide bushing 123 that itextends at a distance from diaphragm 118 so that a stream of air flowingthrough guide bushing 123 impinges against impingement disc I61,producing an impingement pressure acting on the impingement disc 161,which has an unloading effect, via connecting plug 160, on diaphragm 118which acts in the closing direction. The distance between theimpingement disc 16] and diaphragm 118 is so-selected in this case thatthe impingement pressure produced cannot act directly on the closingarea 138 of diaphragm 118.

The mode ofopcration ofthe supply valve according to FIG. 3 differs fromthe mode of operation already described for the supply valve accordingto FIG. 1 only in that diaphragm 118 is unloaded during the flow ofcompressed air with the valve open additionally through theflow-dependent impingement pressure produced by the impingement disc 161so that when magnetic valve 12 is activated to open its valve 61, supplyvalve 2 is capable of closing even more rapidly.

Naturally, a corresponding impingement disc can be built into releasevalve 3, since its unloading effect in the closing direction isdependent only on the presence of a flow of air such as also takes placethrough release valve 3 when the valve is moved to its closed position.

In the examples described, the closing member of the valve is eitherunloaded by the under pressure produced by a turning body (release valve3 according to FIG. 1) or by this and the Ap produced by a throttlebetween the activating pressure and the pressure prevailing in the inletchamber of the valve (supply valve 2 according to FIG. 1) or finally byboth and the impingement pressure (supply valve 103 according to FIG. 3)produced by an impingement body in the closing direction.

Naturally, however, these three flow-dependent unloading possibilitiescan be used individually or in combination and not only for the supplyvalve but also for the release valve of the device described.

In view of the extremely short closing times required for antiskiddevices, this time is even further shortened in the valves described bythe fact that the valves display a diaphragm serving simultaneously as aclosing and activating member with a very small mass which is moreoverpre-unloaded-by a spring.

However, it is possible without difficulty to use the advantagesstemming from a flow-dependent unloading of the closing member in theclosing direction with respect to the achievement of extremely shortclosing times also for valves of different design, particularly forpressure-medium or electromagnetically activated disc valves withseparate activation organs, especially when during the closing of thevalve into the closed position, a flow of pressure medium takes placethrough it.

In the variant examples described, the valve is closable by moving theclosing member against the full pressure of the air stream. Theadvantages of the flowdependent unloading of the closing member in theclosing direction, however, can be achieved without difficulty in valveswhich, with respect to the pressure of the air flow, are completely orpartially pressureequalized.

Having now described the invention, what we claim as new and desire tosecure by Letters Patent, is:

1. For interposition between an inlet conduit and an outlet conduit, aquick closing valve device controlling flow of fluid under pressuretherethrough and comprising:

a. a valve seat,

b. a movable abutment having a chamber on each side thereof and movableinto contact with said seat to cut off flow of fluid under pressure fromthe inlet conduit to the outlet conduit and out of contact with saidseat to provide for flow of fluid under pressure from the inlet conduitto the outlet conduit,

c. valve means operative to control the flow of fluid under pressure toa chamber at one side of said abutment and the release of fluid underpressure from said one side to atmosphere, and wherein the improvementcomprises:

d. flow deflecting means for controlling flow of fluid under pressurefrom the inlet conduit to a chamber at the other side ofsaid abutmentand thence to the outlet conduit in such a manner that the flow of fluidunder pressure therethrough causes a reduction of pressure in saidchamber at said other side of said abutment to render the fluid underpressure supplied to said chamber at said one side effective to movesaid abutment with a snap-action movement into contact with said valveseat to cut off flow of fluid under pressure from the inlet conduit tothe outlet conduit.

2. A quick closing valve device, as recited in claim I, furthercharacterized in that said flow deflecting means comprises a hollowannular truncated cone-shaped member having an outturned flangeintegralwith its larger end and disposed in abutting relationship withthe periphery of said movable abutment, said hollow annular truncatedcone-shaped member being so disposed as to extend in the direction awayfrom said movable abutment and toward said valve seat whereby saidabutment is moved into abutting relationship with the interior of saidhollow annular truncated cone-shaped member upon movement into contactwith said valve seat.

3. A quick closing valve device, as recited in claim 1, furthercharacterized in that said movable abutment has formed integraltherewith on said other side thereof a coaxial concave dished cone withits apex extending in the direction of said valve seat which cone iseffective, prior to movement of said abutment into contact with saidvalve seat, to deflect fluid under pressure in the direction of saidseat.

4. A quick closing valve device, as recited in claim 1, furthercharacterized in that said abutment has formed on said other side a stemintegral therewith and extending from the center thereof in thedirection of said valve seat, and by a member carried adjacent theexterior end of said stem and so disposed as to be subject to fluidunder pressure flowing to the outlet conduit which fluid under pressureis effective via said member and said stem to transmit a force to saidabutment that acts in the direction to move said abutment toward saidvalve seat.

5. A quick closing valve device, as recited in claim 1, furthercharacterized by choke means so disposed on the inlet side of said flowdeflecting means that the pressure of the fluid supplied from the inletconduit to said chamber at said one side of said abutment exceeds thepressure of the fluid supplied from the inlet conduit to said chamber atsaid other side of said abutment.

6. A quick closing valve device, as recited in claim l, furthercharacterized in -that said movable abutment constitutes a valve forcooperation with said seat to control flow of fluid under pressure fromthe inlet conduit to the outlet conduit.

7. A quick closing valve device, as recited in claim 4, furthercharacterized in that said member comprises an annular disc.

8. A quick closing valve device, as recited in claim 7, furthercharacterized in that said abutment comprises a diaphragm constructed ofan elastic material.

9. A quick closing valve device, as recited in claim 8, furthercharacterized by a sectionalized casing having a pair of easing sectionsbetween which the outer periphery of said diaphragm is clamped, one ofsaid casing sections being provided with an internal conical surfaceagainst which one side of said diaphragm normally abuts whereby theeffective area of said diaphragm is increased as said one side thereofis moved away from said conical surface in response to the supply offluid under pressure to said chamber at said one side.

1. For interposition between an inlet conduit and an outlet conduit, aquick closing valve device controlling flow of fluid under pressuretherethrough and comprising: a. a valve seat, b. a movable abutmenthaving a chamber on each side thereof and movable into contact with saidseat to cut off flow of fluid under pressure from the inlet conduit tothe outlet conduit and out of contact with said seat to provide for flowof fluid under pressure from the inlet conduit to the outlet conduit, c.valve means operative to control the flow of fluid under pressure to achamber at one side of said abutment and the release of fluid underpressure from said one side to atmosphere, and wherein the improvementcomprises: d. flow deflecting means for controlling flow of fluid underpressure from the inlet conduit to a chamber at the other side of saidabutment and thence to the outlet conduit in such a manner that the flowof fluid under pressure therethrough causes a reduction of pressure insaid chamber at said other side of said abutment to render the fluidunder pressure supplied to said chamber at said one side effective tomove said abutment with a snap-action movement into contact with saidvalve seat to cut off flow of fluid under pressure from the inletconduit to the outlet conduit.
 2. A quick closing valve device, asrecited in claim 1, further characterized in that said flow deflectingmeans comprises a hollow annular truncated cone-shaped member having anoutturned flange integral with its larger end and disposed in abuttingrelationship with the periphery of said movable abutment, said hollowannular truncated cone-shaped member being so disposed as to extend inthe direction away from said movable abutment and toward said valve seatwhereby said abutment is moved into abutting relationship with theinterior of said hollow annular truncated cone-shaped member uponmovement into contact with said valve seat.
 3. A quick closing valvedevice, as recited in claim 1, further characterized in that saidmovable abutment has formed integral therewith on said other sidethereof a coaxial concave dished cone with its apex extending in thedirection of said valve seat which cone is effective, prior to movementof said abutment into contact with said valve seat, to deflect fluidunder pressure in the direction of said seat.
 4. A quick closing valvedevice, as recited in claim 1, further characterized in that saidabutment has formed on said other side a stem integral therewith andextending from the center thereof in the direction of said valve seat,and by a member carried adjacent the exterior end of said stem and sodisposed as to be subject to fluid under pressure flowing to the outletconduit which fluid under pressure is effective via said member and saidstem to transmit a force to said abutment that acts in the direction tomove said abutment toward said valve seat.
 5. A quick closing valvedevice, as recited in claim 1, further characterized by choke means sodisposed on the inlet side of said flow deflecting means that thepressure of the fluid supplied from the inlet conduit to said chamber atsaid one side of said abutment exceeds the pressure of the fluidsupplied from the inlet conduit to said chamber at said other side ofsaid abutment.
 6. A quick closing valve device, as recited in claim 1,further characterized in that said movable abutment constitutes a valvefor cooperation with said seat to control flow of fluid under pressurefrom the inlet conduit to the outlet conduit.
 7. A quick closing valvedevice, as recited in claim 4, further characterized in that said membercomprises an annular disc.
 8. A quick closing valve device, as recitedin claim 7, further characterized in that said abutment comprises adiaphragm constructed of an elastic material.
 9. A quick closing valvedevice, as recited in claim 8, further characterized by a sectionalizedcasing having a pair of casing sections between which the outerperiphery of said diaphragm is clamped, one of said casing sectionsbeing provided with an internal conical surface against which one sideof said diaphragm normally abuts whereby the effective area of saiddiaphragm is increased as said one side thereof is moved away from saidconical surface in response to the supply of fluid under pressure tosaid chamber at said one side.